Multiple Rotation Interface

ABSTRACT

A simultaneous multiple rotation interface where a series of discs eccentrically rotate about a central shaft to create a speed reduction between an input disc and an output disc. Each disc is engaged with the other via a series of bearings embedded within each disc.

CROSS-REFERENCE TO PRIOR APPLICATION

This application is a divisional of U.S. patent application Ser. No. 10/869,303, filed Jun. 16, 2004.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention generally relates to a simultaneous multiple rotation interface system. In particular, the present invention relates to a simultaneous multiple rotation interface wherein power is transmitted from an input to an output by a series of loosely seeded bearings acting in concert to provide for an extremely efficient, exceptionally powerful system.

2. Background Information

There are several types of rotation interfaces on the market today. Most commonly, these interfaces are found in speed reducers or gearboxes. Common examples of such products include: worm gear reducers, helical gear reducers, spur gear reducers, coaxial reducers, and planetary reducers. These devices are used in several areas of industry, including manufacturing, transportation, automotive, and hardware. However, all of these known products are limited in view of the present invention. Most importantly, these products do not incorporate the used of precisely aligned, seeded bearings as a mechanism to transfer power between an input and an output. This feature makes the present invention superior in view of known prior art devices.

The novel design of applicant's present invention overcomes the problems associated with products known in the art. For example, known rotation interfaces depend on gears, pins, or teeth to transfer power from an input to an output. As such, when these products fail, it is often the result of these teeth, pins, or gears giving way to the shear stress resulting from impact loading exerted upon them. In fact, it is well known in the art that the primary cause of failure in typical gearboxes is tooth breakage, or accelerated wear associated with high speed pinions. This problem is exaggerated in the common case of impact loading. However, the present invention handles these damaging forces extremely well. Bearings are relied upon to withstand such forces; because these bearings are able to rotate, or “give, ” and because the force is distributed evenly among all bearings, the invention is able to withstand forces that the prior art cannot.

Friction breakdown is a common problem associated with currently available rotation interfaces. There is some degree of friction along all moving internal parts, as such, regular lubrication maintenance is essential. Without such lubrication, friction build-up would surely cause a breakdown of the device from the inside out. However, the present invention reduces virtually all internal friction as it relies on a series of reliable, highly durable bearings to transfer power. Employment of such bearings reduces “sliding part” friction because these bearings effectively bear the brunt of competing forces acting on the device. Further, these bearings are aligned so that forces acting on the system are evenly distributed among all of the bearings. Elimination of “sliding part” friction and effective force distribution among all bearings provides for an exceptionally efficient device with an extremely long working life.

Another problem associated with available rotation interfaces is loss of mechanical efficiency. Often poor design, friction, wear and tear, and poor component quality produce a power loss between an input and an output. However, the unique construction of the present invention provides for a negligible power loss between the input and the output. That is, each bearing engages with or “grabs” the second drive at the same precise moment so that each drive is perfectly in sink with the other. Further, each bearing is aligned so as to produce a very tight component fit between the first drive and second drive; as such, there is practically no slack between component parts.

Applicant's invention is extremely cost-effective in view of known prior art. The novel design of Applicant's invention provides for a manufacturing process that is relatively simple and cost effective. As such, the present invention is much less expensive than presently known, similar products. Applicant's invention, when incorporated as part of a larger, more expensive system, can greatly reduce the “component part” cost of the system. Also, Applicant's invention can readily be incorporated with less expensive products that would otherwise be cost prohibitive. In addition, the costs of known devices increases in nonlinear fashion as rotation interfaces are manufactured to provide for double or triple speed reductions; however, the present invention, through it novel design, produces single, double, or triple speed reduction while avoiding soaring production costs.

In view of the limitations of the known prior art, there is a great need for a rotation interface that is low friction, durable, mechanically efficient, and cost-effective. Applicant's invention, by its novel design and straightforward manufacturing process, provides an improved substitute for prior art devices.

SUMMARY OF THE INVENTION

In view of the foregoing, it is an object of the present invention to provide a device that produces double or triple speed reductions inexpensively.

It is another object of the present invention to provide a device that has an extremely high power to weight ratio.

It is another object of the present invention to provide a device with extremely high mechanical efficiency.

It is another object of the present invention to provide a device that is highly cost-effective.

It is another object of the present invention to provide a device that is extremely durable.

It is another object of the present invention to provide a device having a straightforward manufacturing process.

It is another object of the present invention to provide a device that can withstand extreme shear stresses generated by impact loading.

It is another object of the present invention to provide a device that has exceptionally low internal friction.

In satisfaction of these and other related objectives, the present invention provides a novel system to achieve an input/output rotation speed differential. The present invention provides for a highly efficient, exceptionally powerful, durable, and cost-effective interface. As will be discussed in the specification to follow, practice of the present invention involves a combination of components so aligned to provide efficient operation of any number of different devices.

The preferred embodiment of the present invention incorporates a series of discs that rotate about a central pin and within the inner circumference of a radial cage. An input and an output shaft are centrally, axially aligned along the central pin and effectively sandwich the series of discs between one another.

In this embodiment, an input shaft is attached to an input disc that is characterized by a centrally aligned portion and an eccentric flange extending therefrom. The eccentric flange is axially aligned, but centrally offset from the central shaft so that a large radius extends in one direction, and a small radius extends in the opposite direction. As such, as the eccentric flange rotates about the central pin, the circle formed about the diameter of the eccentric flange sweeps around the centrally aligned portion of the disc in eccentric fashion, at reduced speed.

A first driver disc is mated with the input disc through a series of radially aligned, embedded bearings. The first driver disc is characterized by an enlarged inner circumference that allows for eccentric rotation about the central pin. Bearings are positioned between the discs so that the first driver disc may follow the eccentric rotation of the eccentric flange. As the first driver disc is mated with the input disc eccentric flange, it eccentrically rotates about the central pin. In addition, the first driver disc is engaged with a centrally aligned, intermediate disc. Both the first driver disc and the intermediate disc rotate at a speed equal to the input rotational speed by the reciprocal of the number of radially aligned bearings between the input disc and first driver disc.

The intermediate disc also is characterized by a centrally aligned portion, and a centrally offset, eccentric flange. By the same operation as above, the circle formed about the diameter of the second eccentric flange sweeps out along the radius of the centrally aligned portion, at a reduced speed. As seen before, the second eccentric flange engages a second driver that rotates about central pin in eccentric fashion at a further reduced speed. Finally, the second driver disc is engaged with centrally aligned output disc through a series of loosely embedded bearings. These bearings are positioned to allow for the eccentric motion of the second driver disc and the central position of the output disc.

In summary, the first driver disc rotates about the central pin at a reduced speed by virtue of its eccentric motion, caused by engagement with the input shaft eccentric flange. However, the first driver disc remains engaged with centrally aligned components, specifically the intermediate disc, through loosely seeded bearings. The intermediate disc centrally rotates about the central pin, sharing the reduced speed of the first driver disc. This speed reduction operation is carried out a second time on a second driver disc. The second driver disc eccentrically rotates about the central pin, at a further reduced speed, by virtue of its engagement with the intermediate disc eccentric flange. Moreover, the second driver disc remains engaged with, and shares the same rotational velocity as a centrally aligned output disc. Again, this is made possible by the radially aligned, loosely seeded bearings between the two discs.

An important feature associated with the rotation interface of the present invention is that the rotational speed reduction along the interface is equal to the reciprocal of the number of bearings along the interface. As such, any number of combinations can be assembled from reduction stage to reduction stage to easily produce almost any differential between input and output speed.

BRIEF DESCRIPTION OF THE DRAWINGS

Applicant's invention may be further understood from a description of the accompanying drawings, wherein unless otherwise specified, like referenced numerals are intended to depict like components in the various views.

FIG. 1 is a cross sectional view of an embodiment of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring to FIG. 1, an embodiment of the present invention is generally referred to as device 100. Device 100 contains a central pin 112. In the preferred embodiment, central pin 112 is centered about and runs through central shaft 114. Central pin 112 is responsible for holding input 116 and output 118 axially, centrally aligned with respect to one another.

Both input 116 and output 118 contain radial flange 120 and 133, respectively. Radial flange 120 and radial flange 122 each have central pin, receiving means 124 that slideably receives central pin 112, and is configured to allow radial pin 112 to freely rotate within radial flange 120 and 122. In the preferred embodiment, central pin receiving means is a cylindrical-shaped shell, bored out of flanges 120 and 122, with a diameter sized so as to allow central pin 112 to fit within receiving means 124 and rotate freely thereof.

Input disc 125 is attached to input 116. As will be further discussed, input disc is characterized by a centrally aligned tip portion 126 and an eccentric portion 127. Input disc 125 is centrally, axially aligned with input 116 so as to share the same rotational speed as input 116. That is, input 116 and input disc 125 may simply be welded together along the union between input 116 and input disc 125 to provide uniform rotation. Input disc 125 further contains bearing groove 128. Bearing groove 128 runs along the outer circumference of disc 125 in ring-like fashion, and is of a concave, half-circle shape. Bearing groove 128 receives input disc bearings 130 and allows bearings 130 to rotate about an axis parallel to central pin 112. Bearings 130 surround disc 125, remaining loosely embedded within groove 128 so as to allow disc 125 to rotate freely with respect to radial cage 134 and radial cage support frame 132.

Disc 125 is characterized by centrally aligned portion 126 and eccentric flange 127. Central portion 126 is centrally, axially aligned with central pin 112, so arranged that its radius is fixed within its plane of rotation. Disc 125 is further characterized by eccentric radial flange 127. Eccentric radial flange 127 extends from central portion 126, and is axially aligned, but centrally offset with respect to central pin 112. As eccentric flange 127 rotates about pin 112, a smaller offset circle sweeps around the larger, uniform radius of 126. This sweeping motion of eccentric flange 127 is the mechanism responsible for providing a reduction in rotational speed through use of device 100.

First driver disc 136 is mated with eccentric flange 127 through a series of bearings 138. Bearings 138 are embedded between flange 127 and disc 136 and positioned between the outside of flange 127 and the inside of disc 136. That is, disc 136 is of a general bowl shape so that bearings 138 rest along the inside rim of disc 136, where bearings 138 are supported along their inside by flange 127. Bearings 138 are embedded between flange 127 and driver disc 136 so as to allow driver disc 136 to follow the eccentric, sweeping motion of flange 127. Disc 136 is axially aligned and centrally offset with respect to central pin 112 and is characterized by an enlarged inner circumference 140. Inner circumference 140 is offset with respect to pin 112 and further allows disc 136 to follow the eccentric rotation of flange 127 and rotate about pin 112 in eccentric fashion.

Disc 136 contains first driver disc bearing slots 142. In the preferred embodiment, bearing slots 142 are radially aligned, are of half-spherical shape, and have a diameter equal to the diameter of bearings 146 and the eccentricity, or offset amount of eccentric flange 127. Such arrangement allows disc 136 to rotate about central pin 112 in eccentric fashion, while remaining engaged with centrally-aligned components within device 100.

Central disc 143 is characterized by centrally aligned portion 144 and eccentric flange 145. Central portion 144 is centrally, axially aligned with central pin 112, so arranged that its radius is fixed within its plane of rotation. Disc 143 is further characterized by eccentric radial flange 145. Eccentric radial flange 145 extends from central portion 144, and is axially aligned, but centrally offset with respect to central pin 112. As eccentric flange 145 rotates about pin 112, a smaller offset circle sweeps around the larger, uniform radius of central portion 144. This sweeping motion of eccentric flange 145 is the mechanism responsible for providing a second reduction in rotational speed between input 116 and output 118. Importantly, first driver disc 136 and central disc 143 share the same rotational speed. That is, disc 136 and disc 144 have each been singly reduced by virtue of the eccentric motion of flange 127.

Second driver disc 150 is mated with eccentric flange 145 through a series of bearings 152. Bearings 152 are embedded between flange 145 and the inside of disc 150. That is, disc 150 is of a general bowl shape so that bearings 152 rest along the inside rim of disc 150, where bearings 152 are supported along their inside by flange 145. Bearings 152 are embedded between flange 145 and driver disc 150 so as to allow second driver disc 150 to follow the eccentric, sweeping motion of flange 145. Disc 150 is axially aligned and centrally offset with respect to central pin 112 and is characterized by an enlarged inner circumference 154. Inner circumference 154 is offset with respect to pin 112 and further allows disc 150 to follow the eccentric rotation of flange 145 and rotate about pin 112 in eccentric fashion.

Disc 150 contains second driver disc bearing slots 156. In the preferred embodiment, bearing slots 156 are radially aligned, are of half-spherical shape, and have a diameter equal to the diameter of bearings 146 and the eccentricity, or offset amount of eccentric flange 145. Such arrangement allows disc 150 to rotate about central pin 112 in eccentric fashion, while remaining engaged with centrally-aligned components within device 100.

Output disc 158 is mated with second driver disc 150 through a series of seeded bearings 160. Output disc 158 contains output driver disc bearing slots 162. In the preferred embodiment, bearing slots 162 are radially aligned, are of half-spherical shape, and have a diameter equal to the diameter of bearings 160 and the eccentricity, or offset amount of eccentric flange 145. Such arrangement allows disc 158 to rotate about central pin 112 while remaining axially, centrally aligned with respect to central pin 112, while remaining engaged with eccentrically rotating first driver disc 150.

Output disc 158 is centrally, axially aligned with output 118 and mates with output 118 so as to share the same rotational speed as output 118. That is, output 118 and output disc 158 may simply be welded together along the union between output 118 and disc 158 to provide uniform rotation. Output disc 158 further contains bearing groove 164. Bearing groove 164 runs along the outer circumference of disc 158 in ring-like fashion, and is of a concave, half-circle shape. Bearing groove 164 receives output disc bearings 166 and allows bearings 166 to rotate about an axis parallel to central pin 112. Bearings 166 surround disc 158, remaining loosely embedded within groove 164 so as to allow disc 158 to rotate freely with respect to radial cage 134 and radial cage support frame 132. Importantly, second driver disc 150 and output disc 158 share the same rotational speed. That is, disc 150 and disc 158 have each been doubly reduced by virtue of the eccentric motion of flange 127 and eccentric flange 145.

Radial cage 134 and radial cage support frame surround the combination of discs mentioned above. Support frame 132 receives radial cage 134 and holds cage 134 fixed parallel to central pin 112. Further, support frame 132 is engaged with input disc 126 and output disc 158 through bearings 130 and bearings 152 respectively. As mentioned, bearings 130 and 152 allow the combination of discs to rotate with respect to both support frame 132 and cage 134.

Although the invention has been described with reference to specific embodiments, this description is not meant to be construed in a limited sense. Various modifications of the disclosed embodiments, as well as alternative embodiments of the inventions will become apparent to persons skilled in the art upon reference to the description of the invention. It is, therefore, contemplated that the appended claims will cover such modifications that fall within the scope of the invention. 

1. A simultaneous multiple rotation interface, comprising: a central shaft; an input disc, said input disc being centrally, axially aligned with said central shaft, said input disc having an eccentric portion; a driver disc, said driver disc being engaged with said eccentric portion of said input disc; an engagement means, said engagement means having a series of loosely seeded bearings; an output disc, said output disc being centrally, axially aligned with said central shaft, said output disc being engaged with said driver disc via said engagement means.
 2. A simultaneous multiple rotation interface, comprising: a central shaft; an input disc, said input disc being centrally, axially aligned with said central shaft, said input disc having an eccentric portion; a first driver disc, said first driver disc being engaged with said eccentric portion of said input disc; a first engagement means, said first engagement means having a series of loosely seeded bearings; a central disc, said central disc being centrally, axially aligned with said central shaft, said central disc being engaged with said first driver disc via said first engagement means, said central disc having an eccentric portion; a second driver disc, said second driver disc being engaged with said eccentric portion of said central disc; a second engagement means, said second engagement means having a series of loosely seeded bearings; an output disc, said output disc being centrally, axially aligned with said central shaft, said output disc being engaged with said second driver disc via said second engagement means. 